U.S. patent number 10,830,366 [Application Number 15/857,107] was granted by the patent office on 2020-11-10 for hydraulic valve for dampening pressure spikes, and associated systems and methods.
This patent grant is currently assigned to Safran Landing Systems Canada Inc.. The grantee listed for this patent is Safran Landing Systems Canada Inc.. Invention is credited to Marin Besliu, Anthony Carr, Graeme Klim.
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United States Patent |
10,830,366 |
Besliu , et al. |
November 10, 2020 |
Hydraulic valve for dampening pressure spikes, and associated
systems and methods
Abstract
Hydraulic valves for dampening pressure spikes and associated
methods are disclosed herein. In one embodiment, a hydraulic valve
for dampening pressure spikes includes a valve body, a poppet at
least partially inside the valve body, and a pilot piston at least
partially inside the valve body and away from the poppet. The pilot
piston contacts the poppet in response to a pressure spike.
Inventors: |
Besliu; Marin (Mississauga,
CA), Klim; Graeme (Beamsville, CA), Carr;
Anthony (Brampton, CA) |
Applicant: |
Name |
City |
State |
Country |
Type |
Safran Landing Systems Canada Inc. |
Ajax |
N/A |
CA |
|
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Assignee: |
Safran Landing Systems Canada
Inc. (Ajax, CA)
|
Family
ID: |
1000005172894 |
Appl.
No.: |
15/857,107 |
Filed: |
December 28, 2017 |
Prior Publication Data
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Document
Identifier |
Publication Date |
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US 20180188749 A1 |
Jul 5, 2018 |
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Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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62441032 |
Dec 30, 2016 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16F
9/466 (20130101); F16K 37/005 (20130101); F16K
17/082 (20130101); F16F 9/512 (20130101); F16K
17/10 (20130101); F16K 17/048 (20130101); F16K
17/26 (20130101); F16L 55/045 (20130101) |
Current International
Class: |
F16K
17/04 (20060101); F16K 17/08 (20060101); F16F
9/512 (20060101); F16F 9/46 (20060101); F16K
17/26 (20060101); F16L 55/045 (20060101); F16K
37/00 (20060101); F16K 17/10 (20060101) |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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488957 |
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Apr 1970 |
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CH |
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102013002425 |
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Apr 2014 |
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DE |
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1458563 |
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Mar 1966 |
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FR |
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2335967 |
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Oct 1999 |
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GB |
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S6011787 |
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Jan 1985 |
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JP |
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Other References
Communication pursuant to Article 94(3) EPC, issued in
corresponding European Application No. 17211102.3 filed Dec. 29,
2017, 7 pages. cited by applicant .
Extended European Search Report dated Jun. 5, 2018, issued in
corresponding European Application No. 17211102.3 filed Dec. 29,
2017, 12 pages. cited by applicant .
Communication pursuant to Article 94(3) EPC, issued in
corresponding European Application No. 17211102.3 filed Dec. 29,
2017, 12 pages. cited by applicant.
|
Primary Examiner: Keasel; Eric
Attorney, Agent or Firm: Christensen O'Connor Johnson
Kindness PLLC
Parent Case Text
CROSS-REFERENCE TO RELATED APPLICATION
This application claims the benefit of U.S. Provisional Application
No. 62/441,032, filed Dec. 30, 2016, the disclosure of which is
incorporated by reference herein in its entirety.
Claims
The embodiments of the invention in which an exclusive property or
privilege is claimed are defined as follows:
1. A hydraulic valve for dampening pressure spikes, comprising: a
valve body; a poppet at least partially configured inside the valve
body, the poppet having an axially located restriction hole and a
plurality of radially located circulation holes; and a pilot piston
at least partially configured inside the valve body and away from
the poppet, the pilot piston having an axially located piston inner
hole and a plurality of radially located circulation holes, wherein
the pilot piston contacts the poppet in response to a pressure
spike, and wherein, at least partially during the pressure spike, a
hydraulic fluid flows through the restriction hole and the
circulation holes of the poppet, and through the piston inner hole
and the circulation holes of the piston.
2. The valve of claim 1, wherein the valve body is generally axial,
wherein the valve body has a flow inlet and a flow outlet, and
wherein the pilot piston is downstream of the poppet.
3. The valve of claim 2, wherein the pilot piston pushes the poppet
upstream in response to the pressure spike.
4. The valve of claim 1, wherein the poppet contacts the valve body
along a sealing surface prior to the pressure spike, and wherein
the poppet does not contact the valve body at least partially
during the pressure spike.
5. The valve of claim 1, wherein the hydraulic fluid flows from the
poppet into the pilot piston only through the restriction hole of
the poppet in absence of the pressure spike.
6. The valve of claim 1, further comprising: a first bias spring
configured to bias the poppet against a sealing surface of the
valve body, and a second bias spring configured to bias the pilot
piston away from the poppet.
7. The valve of claim 6, further comprising a seal configured to
seal a space between the second bias spring and the hydraulic
fluid.
8. The valve of claim 6, further comprising an aperture for venting
a space around the second bias spring.
9. The valve of claim 6, further comprising a stopper having a
surface in contact with the pilot piston, wherein the surface
includes a plurality of grooves.
10. The valve of claim 1, further comprising a first fluid conduit
attached to one side of the valve body and a second fluid conduit
attached to another side of the valve body.
11. A method of for dampening pressure spikes, comprising: flowing
a hydraulic fluid through a valve body, wherein the valve body
carries a poppet and a pilot piston, the poppet having an axially
located restriction hole and a plurality of radially located
circulation holes, and the pilot piston having an axially located
piston inner hole and a plurality of radially located circulation
holes; biasing the poppet against a sealing surface of the valve
body with first biasing means; biasing the pilot piston away from
the poppet with second biasing means; in response to a pressure
spike, moving the pilot piston to contact the poppet, and at least
partially during the pressure spike, flowing the hydraulic fluid
through the restriction hole and the circulation holes of the
poppet, and through the piston inner hole and the circulation holes
of the piston.
12. The method of claim 11, wherein: the first biasing means
includes a first bias spring, and the second biasing means includes
a second bias spring.
13. The method of claim 12, further comprising, in response to the
pressure spike: pushing the poppet away from a sealing surface.
Description
BACKGROUND
Hydraulic systems may produce pressure spikes (also called "water
hammer" spikes or events). These pressure spikes are sometimes
caused by actuation of the components in the hydraulic system
producing fast transient pressure fields travelling through the
system. Generally, the pressure spikes are undesirable because of
possible damage to hydraulic components, cavitation (e.g., at the
pumps), temporary loss of performance of the components, changes in
the properties of the hydraulic fluids, etc. The pressure spikes
can be especially undesirable in the hydraulic systems of vehicles,
for example trucks or airplanes.
Some conventional technologies attempt to reduce pressure spikes by
incorporating mechanical restrictors into hydraulic lines or
hydraulic ports. Such restrictors can be made by reducing pipe
diameter or by inserting, for example, sponge-like or solid objects
into the pipes to increase the resistances (impedances) of the
fluid flow. These restrictors generally reduce the rate of change
of pressure in the hydraulic flow, therefore also reducing the
pressure spikes.
However, these conventional technologies also increase energy
consumption of the hydraulic system by increasing the pressure drop
across these purposely created restrictors. Furthermore, in some
cases the additional flow resistance generates extra heat in the
hydraulic fluid and may also cause silting or fluid leakage in the
system. Additionally, once the conventional flow resistance is
created, it will consistently affect the pressures in the system,
whether the pressure spike is present or not. Accordingly, it would
be advantageous to provide systems for reducing pressure spikes
having improved performance and reduced cost.
DESCRIPTION OF THE DRAWINGS
The foregoing aspects and many of the attendant advantages of the
claimed subject matter will become more readily appreciated with
reference to the following detailed description, when taken in
conjunction with the accompanying drawings, wherein:
FIG. 1 illustrates an arrangement of a hydraulic pressure spike
dampening valve and pipes in accordance with an embodiment of the
present technology.
FIG. 2 illustrates an arrangement of the hydraulic pressure spike
dampening valve and a manifold in accordance with an embodiment of
the present technology.
FIGS. 3-6 are cross-sectional views of a first embodiment of the
hydraulic dampening valve in accordance with the present
technology.
FIGS. 7 and 8 are cross-sectional views of a second embodiment of
the hydraulic dampening valve in accordance with the present
technology.
FIGS. 9 and 10 are cross-sectional views of a third embodiment of
the hydraulic dampening valve in accordance with the present
technology.
FIGS. 11 and 12 are cross-sectional views of a fourth embodiment of
the hydraulic dampening valve in accordance with the present
technology.
DETAILED DESCRIPTION
The following disclosure describes various embodiments of systems
and associated methods relating to reducing pressure spikes, etc. A
person skilled in the art will also understand that the technology
may have additional embodiments, and that the technology may be
practiced without several of the details of the embodiments
described below with reference to FIGS. 1-12.
Briefly described, methods and devices for dampening hydraulic
pressure spikes are disclosed. The pressure spikes may be caused by
actuation of the components in the hydraulic system, for example,
by opening and closing shut-off valves, etc. A hydraulic pressure
spike dampening valve (also referred to as a "valve") in accordance
with an aspect of the disclosure can be installed in line with
hydraulic pipes/hoses or manifolds (collectively, fluid conduits)
that experience pressure spikes ("water hammers," "hydraulic
pressure spikes," or "spikes"). In some embodiments, the valve may
include two spring loaded moving parts: a poppet and a pilot
piston. In absence of the pressure spikes, the poppet and the pilot
piston remain in their respective spring-biased position as the
hydraulic fluid (HF) flows through the valve. When the pressure
spike occurs, the pilot piston can overcome the bias force of its
bias spring, and move into first contacting and then unseating the
poppet from the sealing surface of the valve. Once the poppet is
unseated from its spring-biased position, the cross-sectional area
available for the fluid flow increases, the impedance of the valve
decreases, and, as a result, the flow of the fluid increases.
Without being bound by theory, it is believed that the increased
fluid flow contributes to a faster reduction of the pressure
spikes. In some embodiments, a response time of the valve, i.e.,
the time to unseat the poppet after the pressure spike occurs, can
be relatively short, for example under 100 ms or under 300 ms.
After the transient pressure spike dissipates, the springs can bias
the pilot piston and the poppet back to their home position until
the next pressure spike event.
In some embodiments, an actuator can move the pilot piston and/or
the poppet from one position to another. Some examples of such
actuators are a bellows actuator and a solenoid. In some
embodiments, the actuators may move a spool that opens/blocks flow
paths in the valve, thereby increasing/decreasing flow impedance
and, consequently, the pressure in the hydraulic fluid.
FIG. 1 illustrates an arrangement of a hydraulic pressure spike
dampening valve 100 and a pipe 200 in accordance with an embodiment
of the present technology. The valve 100 is configured to attach to
the pipe (or hose) 200 through a connection 19. The direction of
the flow is denoted as "F." In some embodiments, the valve 100 may
include an aperture 29 for venting the valve.
FIG. 2 illustrates an arrangement of the hydraulic pressure spike
dampening valve 100 and a manifold 300 in accordance with an
embodiment of the present technology. In some embodiments, the
valve 100 is sealed against the manifold 300 with O-rings 20.
First Embodiment
FIGS. 3-6 are cross-sectional views of an embodiment of the
hydraulic dampening valve 100 in accordance with the present
technology. The valve 100 has a valve body 1 that may be made of
aluminum, steel, titanium or other materials. The valve body 1 may
have threaded connections 19 for connecting to hydraulic pipes,
hoses or other hydraulic components. In operation, the hydraulic
fluid HF flows in the direction F from an inlet I to an outlet O.
Under normal conditions, e.g., in absence of pressure spikes, the
hydraulic fluid flows from an inlet I, through a poppet 2, through
a pilot piston 3, and further to an outlet O.
In some embodiments, a spring 10B biases the poppet 2 against a
sealing surface 7 of the valve body 1. As a result, the flow
through the poppet 2 is directed through a restriction hole 6 and
further into a piston inner hole 34 of the pilot piston 3. Some
hydraulic fluid may escape through circulation holes 9 of the
poppet 2 and circulation holes 31 of the pilot piston 3. However,
the sealing surface 7 only allows fluidic communication between the
poppet 2 and the pilot piston 3 through the restriction hole 6. As
a result, the fluid flow through the valve can be generally limited
(constricted).
In some embodiments, a bias spring 10A biases the pilot piston 3
against a stopper 27. Opposing the force of the bias spring 10A,
the pressure in the hydraulic fluid biases the pilot piston away
from the stopper 27, i.e., away from the outlet O and toward the
poppet 2, because of the difference in cross-sectional areas A1 and
A2. For example, the pressure of the hydraulic fluid in a pocket 52
acts against A1 (a smaller cross-sectional area) to bias the pilot
piston 3 toward the stopper 27, while the pressure in the hydraulic
fluid downstream of the pilot piston 3 and inside grooves 50 of the
stopper 27 acts against A2 (a larger cross-sectional area) to bias
the pilot piston 3 toward the poppet 2. Therefore, the resulting
force from the hydraulic pressure over the surfaces A1/A2 biases
the pilot piston upstream, toward the poppet 2. However, in at
least some embodiments, the bias force of the spring 10A exceeds
the bias force caused by the fluid pressure over the surfaces
A1/A2, resulting in a net force that biases the pilot piston 3
against the stopper 27. Therefore, under normal working conditions
and in absence of pressure spikes, the poppet 2 remains biased
toward the sealing surface 7, and the pilot piston 3 remains biased
toward the stopper 27. In some embodiments, a dynamic T-seal 25 and
backup rings 26 can prevent fluid leakage around the pilot piston 3
and into the space that houses the bias spring 10A.
In some embodiments, the poppet 2 and the pilot piston 3 can be
biased with other biasing means. For example, magnetic biasing
means or gas at high pressure in the space of the first and second
bias springs 10A/10B may replace or augment the biasing force of
the bias springs 10A/10B.
FIGS. 4 and 5 illustrate movements of the poppet 2 and the pilot
piston 3 in response to the pressure spikes in accordance with an
embodiment of the present technology. Specifically, FIG. 4
illustrates an initial contact between the pilot piston 3 and the
poppet 2. FIG. 5 illustrates the poppet 2 that is moved further
toward the inlet I by the pilot piston 3.
FIG. 4 illustrates the initial contact between the pilot piston 3
and the poppet 2. In some embodiments, due to a pressure spike, the
bias force of the bias spring 10A is overcome by the pressure of
the hydraulic fluid applied over a net surface A2 minus A1. As a
result, the bias spring 10A compresses, and the pilot piston 3
moves upstream in a direction D to contact the pilot piston 3.
However, in at least some embodiments, the poppet 2 remains biased
against the sealing surface 7. As a result, the entire flow (or
substantially the entire flow, neglecting the flow leakage around
the sealing surface 7) of the hydraulic fluid still passes through
the restriction hole 6.
FIG. 5 illustrates the pilot piston 3 that moved further in a
direction D toward the inlet I, i.e., sufficiently upstream to
unseat the poppet 2 from the sealing surface 7. The pressure spike
that causes the unseating of the poppet 2 is called "cracking
pressure." In some embodiments, the unseating opens additional
paths for the hydraulic fluid to flow from the inlet I to the
outlet O. For example, in addition to the flow path from the
restriction hole 6 of the poppet 2 through the inner hole 34 of the
pilot piston 3, and then further downstream through the pilot
piston 3, the hydraulic fluid can now also flow through the
circulation holes 9 of the poppet 2, through a valve body hole 35,
into the circulation holes 31 of the pilot piston 3, and further
downstream. As a result, in at least some embodiments, the overall
flow through the valve 100 increases, therefore helping to
dissipate the pressure spike faster. In some embodiments, after the
pressure spike has been dissipated, the bias force of the springs
10A, 10B pushes the pilot piston 3 and the poppet 2 against the
stopper 27 and the sealing surface 7, respectively.
In some embodiments, the poppet 2 can be interchangeable, and may
be configurable in view of expected magnitude of pressure spikes.
For example, the size of the restriction hole 6 and/or the
circulation holes 9 may at least in part determine the value of the
cracking pressure. Additionally, the springs 10A, 10B may also be
configurable for a desired cracking pressure.
FIG. 6 is a cross-sectional view of an embodiment of the hydraulic
dampening valve 100. The illustrated valve 100 includes a screen 8
at the inlet I. The screen 8 can include a plurality of apertures
18 (e.g., round holes, elliptical holes, cell openings in porous
material, etc.) that can prevent particles (e.g., debris) from
entering the interior of the valve 100. In some embodiments, the
size of the apertures 18 can be selected to assure that particles
are not trapped inside the restriction hole 6. In some embodiments,
the screen can be secured to a stopper 11 by laser welding.
Under some conditions, the poppet 2 may vibrate or "chatter." In
some embodiments, the chatter can be prevented or at least reduced
by having a piston 12 (also referred to as a "damping device")
inserted into a cylinder 13. In some embodiments, a clearance 16
between the piston 12 and the cylinder 13 causes a viscous friction
in the hydraulic fluid that is inside or around balancing grooves
15. In some embodiments, the clearance 16 between the piston 12 and
the cylinder 13 can be controlled by lapping the mating surfaces.
When the poppet 2 moves axially upstream due to chattering, the
piston 12 is also pushed upstream. When the poppet 2 moves back
downstream, the piston 12 is also pushed downstream by the flow of
hydraulic fluid through apertures 23. However, in at least some
embodiments the chattering of the poppet 2 is reduced due to the
viscous friction of the fluid between the piston 12 and the
cylinder 13.
Second Embodiment
FIGS. 7 and 8 are cross-sectional views of a second embodiment of
the hydraulic dampening valve in accordance with the present
technology. Specifically, FIG. 7 illustrates a flow of the
hydraulic fluid before a bellow shaft 36S contacts the poppet 2,
and FIG. 7 illustrates the bellow shaft 36S that moved poppet 2
toward the inlet I.
FIG. 7 shows a hydraulic valve 400 that includes the poppet 2
seated against the sealing surface 7 by the bias spring 10B. As a
result, the hydraulic fluid flows in the direction F from the inlet
I through the restriction hole 6. In some embodiments, one part of
the hydraulic fluid flows into an outlet port 39, and further to
the outlet O, while another part of the hydraulic fluid flows
through the bellow shaft 36S and into a bellow actuator 36. In some
embodiments, the hydraulic fluid that enters the below actuator 36
also pressurizes the bellow actuator 36. In response, the bellow
actuator 36 expands, pushing the bellow shaft 36S in the direction
D toward the poppet 2. In some embodiments, under normal flow
conditions, the bellow shaft 36S can travel in the direction D to
contact the poppet 2, but cannot unseat the poppet 2 because of the
bias force of the bias spring 10B. In some embodiments, a seal 37
prevents leakage of the hydraulic fluid around the bellow shaft
36S.
FIG. 8 shows the bellow shaft 36S that has travelled in the
direction D sufficiently to unseat the poppet 2. In some
embodiments, the pressure spike may provide sufficient pressure
inside the bellow actuator 36 to overcome the bias force of the
bias spring 10B, and to unseat the poppet 2. When the poppet 2 is
unseated from the sealing surface 7, the hydraulic fluid can also
flow through the holes 9, through the valve body hole 35, and
further into the outlet port 39. In at least some embodiments, thus
increased flow of the hydraulic fluid may be sufficiently high to
cause a relatively rapid dissipation of the pressure spike. In some
embodiments, the pressure spike may substantially dissipate in less
than 300 ms or less than 100 ms. In at least some embodiments,
after the pressure spike has been dissipated, the bias force of the
spring 10B pushes the poppet 2 back against the sealing surface
7.
Third Embodiment
FIGS. 9 and 10 are cross-sectional views of a third embodiment of
the hydraulic dampening valve in accordance with the present
technology. Specifically, FIG. 9 illustrates flow of the hydraulic
fluid before a solenoid shaft 40S unseats the poppet 2, and FIG. 10
illustrates the solenoid shaft 40S that unseated the poppet 2 and
moved it toward the inlet I.
FIG. 9 shows a hydraulic valve 500 that includes the poppet 2
seated against the sealing surface 7 by the bias spring 10B. The
illustrated valve 500 includes a solenoid 40 and the solenoid shaft
40S. Under normal conditions (e.g., no pressure spikes in the
system), the poppet 2 can remain seated against the sealing surface
7, therefore directing substantially entire flow of the hydraulic
fluid through the restriction hole 6 only to the outlet port 39. In
some embodiments, the pressure of the hydraulic fluid can be
monitored by a sensor S connected through a wired or a wireless
data connection with a controller C. In some embodiments, when the
sensor S detects a pressure spike, the controller C sends an
activation signal to an electrical connector 41 that activates the
solenoid 40 to move the solenoid shaft 40S in the direction D.
FIG. 10 shows the poppet 2 that is unseated and moved upstream from
the sealing surface 7 by the solenoid shaft 40S. When the poppet 2
is unseated from the sealing surface 7, the hydraulic fluid can
flow through the holes 9, through the valve body hole 35, and
further into the outlet port 39. In at least some embodiments, this
increased flow of the hydraulic fluid may be sufficiently high to
cause a relatively rapid dissipation of the pressure spike. In some
embodiments, the pressure spike may substantially dissipate in less
than 300 ms or less than 100 ms. In at least some embodiments,
after the pressure spike has been dissipated, the sensor S sends a
corresponding signal to the controller C. In response, the
controller C sends a signal to the solenoid 40 to retract the
solenoid shaft 40S, and the bias force of the spring 10B pushes the
poppet 2 against the sealing surface 7. As a result, the flow of
the hydraulic fluid becomes again restricted till the next pressure
spike.
Fourth Embodiment
FIGS. 11 and 12 are cross-sectional views of a fourth embodiment of
the hydraulic dampening valve in accordance with the present
technology. Specifically, FIG. 11 illustrates a spool 51 in a
position that enables the flow of hydraulic fluid through a flow
path FP1, and FIG. 12 illustrates the spool 51 that enables the
flow of hydraulic fluid through a flow path FP2 in addition to the
flow path FP1.
FIG. 11 shows a hydraulic valve 600 having the flow path FP1 that
connects the inlet I to the outlet O. The flow path FP1 may include
one or more restrictors 49 that limit the flow of hydraulic fluid
through the valve 600. Some examples of the flow restrictors are
solid obstructions, porous obstructions, or pipe narrowing. In some
embodiments, in absence of the pressure spikes, a relatively high
flow resistance of the flow path FP1 results in a relatively low
flow of the hydraulic fluid. In the illustrated embodiment, the
spool 51 blocks (or substantially restricts) hydraulic fluid from
flowing through a flow path FP2.
FIG. 12 shows a hydraulic valve 600 where the hydraulic fluid can
flow in the flow path FP2 in addition to the flow path FP1. As a
result, the overall fluid flow can be greater through the flow
paths FP1 and FP2 than through just the flow path FP1. The spool 51
can be moved in the position that opens the flow path FP2 in
response to the pressure spike detected by the sensor S, and
communicated to the controller C. In some embodiments, the solenoid
shaft 40S moves the spool 51 in the direction D such that the
hydraulic fluid can flow around a smaller diameter d2 of the spool
51, and further toward the outlet port 39. In some embodiments, a
larger diameter d1 of the spool 51 minimizes the leakage of the
hydraulic fluid around the spool. In at least some embodiments,
after the pressure spike has been dissipated, the sensor S sends a
corresponding signal to the controller C, the controller C sends a
deactivation signal to retract the solenoid shaft 40S, and the
spool 51 is moved in the position that keeps the flow path FP1 open
and the flow path FP2 closed.
Many embodiments of the technology described above may take the
form of computer- or controller-executable instructions, including
routines executed by a programmable computer or controller. Those
skilled in the relevant art will appreciate that the technology can
be practiced on computer/controller systems other than those shown
and described above. The technology can be embodied in a
special-purpose computer, controller or data processor that is
specifically programmed, configured or constructed to perform one
or more of the computer-executable instructions described above.
Accordingly, the terms "computer" and "controller" as generally
used herein refer to any data processor and can include Internet
appliances and hand-held devices (including palm-top computers,
wearable computers, cellular or mobile phones, multi-processor
systems, processor-based or programmable consumer electronics,
network computers, mini computers and the like).
From the foregoing, it will be appreciated that specific
embodiments of the technology have been described herein for
purposes of illustration, but that various modifications may be
made without deviating from the disclosure. For example, in some
embodiments, the grooves 50 may be replaced with or augmented by
inclined surfaces that allow hydraulic fluid to enter space between
the stopper 27 and the pilot piston 3. In some embodiments, the
machining roughness can replace the grooves 50. Moreover, while
various advantages and features associated with certain embodiments
have been described above in the context of those embodiments,
other embodiments may also exhibit such advantages and/or features,
and not all embodiments need necessarily exhibit such advantages
and/or features to fall within the scope of the technology.
Accordingly, the disclosure can encompass other embodiments not
expressly shown or described herein.
* * * * *